US5336056A - Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism - Google Patents

Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism Download PDF

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Publication number
US5336056A
US5336056A US07/982,836 US98283692A US5336056A US 5336056 A US5336056 A US 5336056A US 98283692 A US98283692 A US 98283692A US 5336056 A US5336056 A US 5336056A
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United States
Prior art keywords
swash plate
pair
plate assembly
pistons
drive shaft
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Ceased
Application number
US07/982,836
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English (en)
Inventor
Kazuya Kimura
Hiroaki Kayukawa
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Toyota Industries Corp
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Toyoda Jidoshokki Seisakusho KK
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Assigned to KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO reassignment KABUSHIKI KAISHA TOYODA JIDOSHOKKI SEISAKUSHO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAYUKAWA, HIROAKI, KIMURA, KAZUYA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the present invention relates to a variable capacity swash plate type refrigerant compressor mainly used for an airconditioner for a car. More particularly, it relates to a variable capacity single headed piston swash plate type compressor provided with a double fulcrum hinge mechanism able to pivotally support a variable inclination swash plate assembly while preventing an application of an excessive load to a sleeve element on which the variable inclination swash plate assembly is turnably mounted.
  • variable capacity swash plate type compressor having single headed pistons therein.
  • the variable capacity swash plate type compressor of Japanese Unexamined Utility Model Publication '082 includes a cylinder block having a crank chamber formed therein for housing an inclination changeable wobble plate assembly, and a plurality of cylinder bores in which a plurality of single headed pistons are reciprocally fitted, to suck and compress a refrigerant gas and to discharge the compressed refrigerant gas.
  • the wobble plate assembly includes a rotary drive element rotatable with the drive shaft and a swash plate non-rotatably supported on the rotary drive element, and is driven by a rotatably supported axial drive shaft to which a lug member is fixedly attached to be projected radially and rotated together with the drive shaft within the crank chamber.
  • the lug member is operatively connected to the rotary drive element of the wobble plate assembly via a hinge mechanism, and a sleeve element slidably mounted on the drive shaft is also operatively connected to the rotary drive element of the wobble plate assembly.
  • the rotary drive element is able to be rotated together with the drive shaft and to change an angle of inclination thereof from an erect position corresponding to a small compression capacity position to a fully inclined position corresponding to a large compression capacity position.
  • the hinge mechanism includes an elongated guide hole bored through the lug member, and a hinge pin having one end movably fitted in the elongated guide hole of the lug member and the other end fixed to a swing plate member extended from the rotary drive plate.
  • the sleeve element is arranged to be axially slid, and provided with a lateral pin radially projected therefrom to form trunnion pins about which the rotary drive plate is pivotally mounted.
  • the swash plate of the wobble plate assembly is operatively connected to the plurality of pistons via respective piston rods having ball-and-socket joints on both ends, and thus, when the drive shaft is rotated, the rotation of the drive shaft and the rotary drive element is converted into a reciprocation of the respective pistons in the cylinder bores.
  • the cylinder block has a communication passageway formed therein and extended between the crank chamber and a suction chamber, for receiving therein the refrigerant gas before compression and an extent of the communication between the abovementioned two chambers is controlled by a capacity control valve.
  • the refrigerant gas before compression is pumped from the suction chamber into the cylinder bores, to be compressed by the pistons during the suction and compression strokes of the pistons, and the compressed gas is discharged from the cylinder bores toward a discharge chamber for the refrigerant gas after compression.
  • a force consisting of first and second forces acts on the wobble plate assembly from the pistons, as a reaction of the compression and suction of the refrigerant gas by the pistons, and the wobble plate assembly is physically supported by the hinge mechanism at a fulcrum position thereof at which the hinge pin is in contact with the guide wall of the elongated guide hole of the lug member.
  • the construction of the above-mentioned hinge mechanism including the projected lug member radially projected from the drive shaft and the hinge pin in engagement with the elongated hole of the lug member results in an arrangement such that the fulcrum position of the hinge mechanism is moved around the axis of the drive shaft so as to constantly correspond to a given position of the swash plate at which the swash plate is connected to one of the pistons moved in the cylinder bore to the top dead center "T" thereof from the bottom dead center "B,” thereof, as diagrammatically illustrated in FIG. 6 of the accompanying drawings, during the rotation of the rotary drive element of the wobble plate assembly.
  • the total force of the first and second forces acting from each piston on the wobble plate assembly is concentrated at a position of the assembly shifted from the fulcrum position "P" of the hinge mechanism in a direction of the rotation of the rotary drive plate of the wobble plate assembly, and an amount of the shift depends on the number of rotations of the drive shaft, and the compression ratio of the refrigerant gas or the angle of inclination of the wobble plate assembly. Therefore, the wobble plate assembly supported by the fulcrum position of the hinge mechanism must be subjected to a bending moment due to the shifting of the position at which the total force of the first and second reaction forces acts on the wobble plate assembly from the fulcrum position of the hinge mechanism.
  • This bending moment acting on the wobble plate assembly is absorbed by the sleeve element to thereby apply an excessive local force to the sleeve element, and as a result, an abnormal noise is generated when the sleeve is slid on the drive shaft and the physical durability of the sleeve element is reduced.
  • an object of the present invention is to obviate the problems encountered by the abovementioned variable capacity-single headed piston swash plate type refrigerant compressor according to the prior art.
  • Another object of the present invention is to provide a variable capacity single headed piston swash plate type compressor provided with a novel double fulcrum type hinge mechanism for pivotally supporting a variable inclination rotary swash plate assembly in a manner such that a load applied to a slidable sleeve element on which the swash plate is turnably mounted is reduced when a force consisting of reaction forces of compression and suction of a refrigerant gas is imposed on the swash plate by pistons reciprocating in cylinder bores.
  • variable capacity single headed piston swash plate type compressor including:
  • an axially extended cylinder block having front and rear ends thereof and a plurality of axial cylinder bores formed therein;
  • a front housing sealingly connected to the front end of the cylinder block and defining a closed crank chamber therein extending in front of ends of the cylinder bores;
  • a rear housing connected to the rear end of the cylinder block and defining therein a suction chamber for a refrigerant gas before compression and a discharge chamber for the refrigerant gas after compression;
  • a drive shaft rotatably held by the cylinder block and the front housing and having an axis thereof axially extended through the crank chamber;
  • a rotary support element mounted on the drive shaft to be rotated therewith in the crank chamber
  • variable inclination rotary swash plate assembly pivotally held by a hinge means and slidably mounted around the drive shaft via a slidable sleeve element and capable of turning about an axis perpendicular to the axis of the drive shaft to thereby vary an angle of inclination thereof;
  • a control valve means for adjusting a fluid pressure in the crank chamber to thereby control a capacity of the compressor
  • the hinge means is provided with a pair of hinges to provide two fulcrum positions about which the swash plate assembly is pivotally hinged, the two fulcrum positions being arranged to be spaced apart from one another with respect to a center position which lies in a plane including the axis of the drive shaft and passing through a predetermined position of the swash plate assembly at which the swash plate assembly is engaged with one of the plurality of pistons brought to a top dead center thereof.
  • the two fulcrum positions of the hinge mean are symmetrically arranged on opposite sides of the plane passing through the predetermined position of the swash plate assembly at which the swash plate assembly is engaged with one of the plurality of pistons moved to a top dead center thereof, one of the two fulcrum positions appropriately absorbs a reaction force of the compression of the refrigerant gas acting from the pistons on the swash plate assembly while the other of the two fulcrum positions appropriately absorbs a reaction force of the suction of the refrigerant gas acting from the pistons on the swash plate assembly.
  • the hinge means having the two fulcrum positions always can absorb a total force of the reaction forces of the compression and suction of the refrigerant gas, so that the swash plate assembly is not subjected to an unfavorable bending moment, and thus a local load is not applied to the sleeve element.
  • FIG. 1 is a cross-sectional view of a variable capacity single headed piston swash plate type compressor provided with a double fulcrum hinge means according to a first embodiment of the present invention
  • FIG. 2 is a partial cross-sectional view taken along the line II--II of FIG. 1;
  • FIG. 3 is a diagrammatical view indicating a relationship between the time and position of a piston with respect to the compressor according to the present invention
  • FIG. 4 is a cross-sectional view of a variable capacity single headed piston swash plate type compressor provided with a double fulcrum hinge means according to a second embodiment of the present invention
  • FIG. 5 is a partial cross-sectional view taken along the line V--V of FIG. 4;
  • FIG. 6 is a diagrammatical view indicating a relationship between the time and position of a piston with respect to the compressor according to the prior art.
  • variable capacity swash plate type refrigerant compressor of a first embodiment of the present invention will be provided below with reference to FIGS. 1 through 3.
  • variable capacity swash plate type refrigerant compressor of the first embodiment has a cylinder block 1 having a plurality of cylinder bores 1a, and front and rear ends of the cylinder block 1 are sealingly closed by front and rear housings 2 and 3.
  • the cylinder block 1 and the front housing 2 defines an air-tight sealed cylindrical crank chamber 2a therebetween to house a swash plate assembly including a cylindrical rotary drive element 11 and a swash plate 15 therein.
  • a valve plate 12 is intervened between the rear end of the cylinder block 1 and the rear housing 3 having formed therein a suction chamber 3a and a discharge chamber 3b which can be communicated with the cylinder bores 1a of the cylinder block 1 via suction and discharge valve mechanisms, respectively.
  • An axial drive shaft 4 is centrally arranged to extend through the front housing 2 and the cylinder block 1, and rotatably supported by bearings mounted in the front housing 2 and the cylinder block 1.
  • a front end of the drive shaft 4 is outwardly extended from the front housing 2 to be connectable to a drive source such as a car engine, and a rear end of the drive shaft 4 is rotatably supported by the bearing in the cylinder block 1.
  • a rotary support 5 is fixedly mounted on the drive shaft 4 in the crank chamber 2a to be rotatable with the drive shaft 4.
  • the rotary support 5 is axially supported by a thrust bearing seated on an inner end of the front housing 2, and has rearwardly extended two support arms 6 for supporting a cylindrical rotary drive element 11 of the swash plate assembly via a hinge means having a pair of hinges designated by "K", as shown in FIG. 2.
  • the two hinges K provide a pivotal connection between the rotary support 5 and the rotary drive element 11, and are arranged in a manner such that the hinges K are equidistantly spaced from one another with respect to a center position lying in a plane which extends to include therein an axis of the drive shaft 4 and which passes through a predetermined position of the swash plate 15 at which the swash plate 15 is engaged with one of a plurality of pistons 19 brought to a top dead center "T" thereof.
  • the hinge means having the two hinges K is arranged between the two support arms 6 of the rotary support 5 and a front end of the cylindrical drive element 11.
  • both support arms 6 of the rotary support 5 are axially rearwardly extended, and arranged to be symmetrical with respect to the above-mentioned plane including therein the axis of the drive shaft 4 and passing through the predetermined position of the swash plate 15 at which the swash plate 15 is engaged with the piston brought to the top dead center T thereof.
  • Each of the support arms 6 has a through-bore 6a in which a race member 8 is fixedly seated to turnably receive a ball element 9.
  • the ball element 9 has formed therein a through-hole 9a operative as a guide hole permitting an axial slide of a guide pin 10 therein.
  • the guide pins 10 of the two support arms 6 of the pair of hinges K are arranged to be in parallel with one another.
  • the rotary drive element 11 of the swash plate assembly has formed therein two through-bores 11a, in which the guide pins 10 are fixedly press-fitted.
  • the two hinges K of the hinge means define a pair of hinge positions P 1 and P 2 arranged symmetrically with respect to the plane passing through the predetermined position of the swash plate 15 at which the swash plate 15 is engaged with the piston 19 brought to the top dead center thereof.
  • the hinge position P 1 is arranged to present a pivotal connection between one of the support arms 6 of the rotary support 5 and a portion of the rotary drive element 11 of the swash plate assembly, which portion acts to move each single headed piston 19 to an intermediate position of the entire compression stroke thereof
  • the hinge position P 2 is arranged to present a pivotal connection between the other of the support arms 6 of the rotary support 5 and a different portion of the rotary drive element 11 of the swash plate assembly, which portion acts to move each piston 19 to an intermediate position of the entire suction stroke thereof.
  • the swash plate 15 mounted on the rotary drive element 11 is tightly fixed by a ring 16 threadedly engaged with a hub portion of the drive element 11.
  • the swash plate 15 is provided with support rails 15c on both faces thereof extended annularly around the axis of the drive shaft 4, and these support rails 15c are slidably engaged with respective guide grooves of inner shoes 17 having a spherical back face, respectively, and thus the inner shoes 17 are prevented from being shifted in a radial direction of the swash plate 15.
  • the inner shoes 17 are engaged with semi-cylindrical outer shoes 18 in such a manner that the spherical back faces of the inner shoes 17 are in sliding contact with cylindrical inner faces of the outer shoes 18 outer faces of which are also shaped in a cylindrical face, respectively, These cylindrical outer faces of the outer shoes 18 are in sliding contact with cylindrical walls of a cutout 19a of each piston 19.
  • the cutout 19a is recessed in a direction perpendicular to the axis of the piston 19 and provided for permitting a passage of the swash plate 15 therethrough during the rotation of the swash plate 15.
  • the inner and outer shoes 17 and 18 are provided as a motion conversion means for converting the rotation of the inclined swash plate 15 into a reciprocation of each of the pistons 19 in the cylinder bore 1a.
  • the rotary drive element 11 is mounted on a sleeve 13 slidably mounted on the drive shaft 4.
  • the sleeve element 13 is axially slidable on the drive shaft 4 under spring forces of springs 20a and 20b arranged on opposite sides of the sleeve element 13, and an outer spherical face of the sleeve element 13 is in turnable contact with a spherical inner face of the rotary drive element 11,
  • the swash plate 15 of the swash plate assembly can be rotated with the drive shaft 4 via the rotary support 5 and the rotary drive element 11, and turned to change an angle of inclination thereof via the two hinges K of the hinge means and the sleeve element 13.
  • Control valves 21 are provided in the rear housing 3 for adjusting a fluid pressure level within the crank chamber 2a as shown in FIG. 1.
  • the capacity of the compressed refrigerant gas discharged toward the discharge chamber 3b is controlled by adjusting the fluid pressure level within the crank chamber 2a by the control valves 21. Namely, when the fluid pressure level within the crank chamber 2a is lowered by the operation of the control valves 21 with respect to a suction pressure level, a back pressure acting on the respective pistons 19 is reduced, and accordingly, the angle of inclination of the swash plate 15 is increased. Namely, in the respective hinges K of the hinge means, the ball elements 9 of the respective hinges K are turned in the race members 8 while permitting the respective guide pins 10 to slide with respect to the ball elements 9, i.e., the guide pins 10 axially slide through the through-holes 9a of the ball elements 9.
  • the rotary drive element 11 of the swash plate assembly is turned about the sleeve 13 sliding axially in the forward direction against the spring force of the lefthand spring 20b. Accordingly, the angle of inclination of the swash plate 15 with respect to a plane perpendicular to the axis of the drive shaft 4 is increased, and thus the inner shoes 17 of the motion conversion means are slidingly turned in the outer shoes 18 which slide radially with respect to the axis of the respective piston 19. As a result, the stroke of the respective pistons 19 is extended to thereby increase the compression capacity of the compressor.
  • the swash plate 15 reaches the largest inclination position, the largest capacity operation of the compressor is performed.
  • the sleeve element 13 is slid in the rearward direction against the spring force of the righthand spring 20a. Therefore, the guide pins 10 are slidingly moved out of the ball elements 9 to thereby permit the swash plate 15 to turn toward a small inclination angle position thereof, and thus the turning of the inner shoes 17 and the sliding of the outer shoes 18 of the motion conversion means occur to thereby shorten the reciprocating stroke of the respective pistons 19. Accordingly, the compression capacity of the compressor is decreased. When the swash plate 15 reaches the smallest inclination angle position thereof, i.e., an erect position thereof, the smallest capacity operation of the compressor is performed.
  • one of the hinges K of the hinge means having the hinge position P 1 contributes to the absorbing of the entire reaction forces acting from the respective pistons 19 in the compression stroke thereof on the swash plate 15 via the motion conversion means in response to the compression of the refrigerant gas by these pistons 19 in the compression stroke thereof
  • the other hinge K of the hinge means having the hinge position P 2 contributes to the absorbing of the entire reaction forces acting from the respective pistons 19 in the suction stroke thereof on the swash plate 15 via the motion conversion means in response to the suction of the refrigerant gas by these pistons 19 in the suction stroke thereof.
  • the two hinges K of the hinge means can cooperate to provide a constant contribution to the absorbing of the reaction forces of the compression and suction of the refrigerant gas during a complete rotation of the swash plate assembly, the swash plate 15 of the swash plate assembly is not subjected to an unfavorable bending moment, and thus the sleeve element 13 on which the assembly is turnably mounted does not suffer from an application of a local load by the swash plate assembly. Namely, the sleeve element 13 is able to permit a smooth turn of the swash plate assembly, which is constantly maintained in a spherical contact with the outer spherical face of the sleeve element 13.
  • the cooperation of the double fulcrum hinge means having the pair of hinges K arranged to be equidistantly spaced from the plane including the axis of the drive shaft and passing the predetermined position of the swash plate 15 at which the swash plate 15 is engaged with one of the single headed pistons 19 brought to the top dead center "T" thereof, and the sleeve element 13 having the spherical outer face in a spherical contact with the swash plate assembly enables an elimination of the conventional sleeve pins arranged between the conventional sleeve element and the wobble plate assembly to absorb a bending moment acting on the wobble plate assembly.
  • the sleeve element 13 employed for the compressor of the present invention can avoid a local abrasion thereof, and exhibit a long operation life without causing noise during the operation of the compressor.
  • a cylinder block 31 having a plurality of cylinder bores 31a, and front and rear ends of the cylinder block 31 are sealingly closed by front and rear housings 32 and 33.
  • the cylinder block 31 and the front housing 32 defines an air-tight sealed cylindrical crank chamber 32a therebetween to house a swash plate assembly including a swash plate 37 therein.
  • a valve plate 40 is intervened between the rear end of the cylinder block 31 and the rear housing 33 having formed therein a suction chamber 33a and a discharge chamber 33b which can be communicated with the cylinder bores 31a of the cylinder block 31 via suction and discharge valve mechanisms, respectively.
  • An axial drive shaft 34 is centrally arranged to extend through the front housing 32 and the cylinder block 31, and rotatably supported by bearings mounted in the front housing 32 and the cylinder block 31.
  • a front end of the drive shaft 34 is outwardly extended from the front housing 32 to be connectable to a drive source such as a car engine, and a rear end of the drive shaft 34 is rotatably supported by the bearing in the cylinder block 31.
  • a rotary support 35 is fixedly mounted on the drive shaft 4 in the crank chamber 32a to be rotatable with the drive shaft 34.
  • the rotary support 35 is axially supported by a thrust bearing seated on an inner end of the front housing 32, and has two rearwardly extended support arms 35a for pivotally supporting the swash plate assembly via a hinge means having a pair of hinges designated by "M", as shown in FIG. 5.
  • the two hinges M provide a pivotal connection between the two support arms 35a of the rotary support 35 and a pair of swing plates 37a fixed to the swash plate assembly, and are arranged in a manner such that the hinges M are equidistantly spaced from one another with respect to a center position lying in a plane which extends to include therein an axis of the drive shaft 34 and pass through a predetermined position of the swash plate 37 at which the swash plate 37 is engaged with one of a plurality of pistons 38 brought to a top dead center "T" thereof.
  • the hinge means having the pair of hinges M is arranged between the two support arms 35a of the rotary support 35 and front ends of the pair of swing plates 37a.
  • Both support arms 35a of the rotary support 35 are axially rearwardly extended, and arranged to be symmetrical with respect to the above-mentioned plane including therein the axis of the drive shaft 34 and passing through the predetermined position of the swash plate 37 at which the swash plate 15 is engaged with the piston 38 brought to the top dead center "T" thereof.
  • the support arms 35a have an elongated through-bore 35b. respectively, in which an end of each of a pair of hinge pins 37b is engaged. The other end of each of the hinge pins 37b is fixed to the associated one of the pair of swing arms 37a of the swash plate 37.
  • the hinge pins 37b of the hinges "M" of the present embodiment are arranged to be coaxial with each other in a direction vertical to the axis of the drive shaft 34 as clearly illustrated in FIG. 6.
  • fulcrum positions P 1 and P 2 of the pair of hinges M are arranged to be symmetrical with respect to a plane extending to include therein an axis of the drive shaft 34 and passing through a predetermined position of the swash plate 37 at which the swash plate 37 is engaged with one of a plurality of pistons 38 brought to the top dead center "T" thereof.
  • the fulcrum positions P 1 and P 2 of the pair of hinges "M” can act in the same manner as those of the pair of hinges "K" of the first embodiment of FIGS.
  • the hinge position P 1 provides a pivotal connection between one of the support arms 35a of the rotary support 35 and one of the swing arms 37a of the swash plate 37, acting to move each single headed piston 38 to an intermediate position of the entire compression stroke thereof
  • the hinge position P 2 provides a pivotal connection between the other of the support arms 35a of the rotary support 35 and the other of the swing arms 37a of the swash plate 37, acting to move each piston 19 to an intermediate position of the entire suction stroke thereof.
  • the swash plate 37 has flat faces on opposite sides thereof, and is mounted around the drive shaft 34 via a sleeve element 36 slidably mounted on the drive shaft 34.
  • the sleeve element 36 has formed therein a spherical outer face in spherical contact with a central hub portion of the swash plate 37. Therefore, the swash plate 37 can be rotated together with the drive shaft 34 and turned about the sleeve element 36 to change an angle of inclination thereof with respect to a plane perpendicular to the axis of the drive shaft 34.
  • the swash plate 37 is operatively engaged with the plurality of single headed pistons 38 reciprocatorily fitted in the cylinder bores 31a of the cylinder block 31 via respective pair of shoes 39.
  • Each shoe 39 has a flat face in contact with one of the flat faces of the swash plate 37, and a spherical face in turnable contact with a spherical recess provided in a radial cutout of each piston 38.
  • the radial cutout of each piston 38 is arranged in an end of the piston opposite to a compressing end face of the piston 38.
  • the compressor of FIG. 4 is provided with a control valve 41 arranged in the cylinder block 31 for controlling fluid communication between the crank chamber 32a and the suction chamber 33a to thereby adjust fluid pressure level in the crank chamber 32a.
  • one of the hinges M of the hinge means having the hinge position P 1 contributes to the absorbing of the entire reaction forces acting from the respective pistons 38 in the compression stroke thereof on the swash plate 37 via the motion conversion means in response to the compression of the refrigerant gas by these pistons 38 in the compression stroke thereof
  • the other hinge M of the hinge means having the hinge position P 2 contributes to the absorbing of the entire reaction forces acting from the respective pistons 38 in the suction stroke thereof on the swash plate 37 via the motion conversion means in response to the suction of the refrigerant gas by these pistons 38 in the suction stroke thereof.
  • the two hinges M of the hinge means can cooperate to provide a constant contribution to the absorbing of the reaction forces of the compression and suction of the refrigerant gas during a complete rotation of the swash plate assembly, the swash plate 37 of the swash plate assembly is not subjected to an unfavorable bending moment, and thus the sleeve element 36 on which the assembly is turnably mounted does not suffer from an application of a local load by the swash plate assembly. Namely, the sleeve element 36 is able to permit a smooth turn of the swash plate 37 constantly maintained in a spherical contact with the outer spherical face of the sleeve element 36.
  • the pair of fulcrum positions P 1 and P 2 of the hinges "K” or “M” may be arranged to be assymmetrical with respect to a plane extending to include the axis of the drive shaft and passing through a predetermined position of the swash plate 15 or 37 at which the swash plate is engaged with one of the single headed pistons 19 or 38 brought to a top dead center thereof as required.
  • the described double fulcrum hinge means is incorporated in a variable capacity swash plate type refrigerant compressor having a swash plate rotated together with the drive shaft, but the double fulcrum hinge means may also be incorporated in a variable capacity swash plate type refrigerant compressor having a swash plate assembly including a non-rotatable wobble plate for driving the reciprocation of the single headed pistons.
  • a double fulcrum hinge means for providing a pivotal support between a rotary support of a drive shaft and a variable inclination swash plate assembly has a pair of fulcrum positions
  • the hinge means is able to absorb the reaction forces of the compression and suction of a refrigerant gas without applying a local load to a sleeve element on which the swash plate assembly is turnably mounted. Therefore, the sleeve element does not suffer from a local abrasion, and can smoothly and turnably support the swash plate increasing the operational life of the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
US07/982,836 1991-03-30 1992-03-27 Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism Ceased US5336056A (en)

Applications Claiming Priority (3)

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JP3-067365 1991-03-30
JP3067365A JP2626292B2 (ja) 1991-03-30 1991-03-30 容量可変型斜板式圧縮機
PCT/JP1992/000384 WO1992017705A1 (en) 1991-03-30 1992-03-27 Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism

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US5336056A true US5336056A (en) 1994-08-09

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US07/982,836 Ceased US5336056A (en) 1991-03-30 1992-03-27 Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism
US08/693,483 Expired - Lifetime USRE35878E (en) 1991-03-30 1992-03-27 Variable capacity swash plate type refrigerant compressor having a double fulcrum hinge mechanism

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JP (1) JP2626292B2 (enrdf_load_stackoverflow)
KR (1) KR960001567B1 (enrdf_load_stackoverflow)
DE (2) DE4290950T1 (enrdf_load_stackoverflow)
WO (1) WO1992017705A1 (enrdf_load_stackoverflow)

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US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
US5540559A (en) * 1993-04-08 1996-07-30 Ube Industries, Ltd. Variable capacity swash-plate type compressor
US5573379A (en) * 1994-04-21 1996-11-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash plate type compressor
EP0748936A1 (en) * 1995-06-05 1996-12-18 Calsonic Corporation Variable displacement swash plate type compressor
EP0759505A3 (en) * 1995-07-27 1997-03-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US5638736A (en) * 1994-06-07 1997-06-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wave cam type compressor
FR2760257A1 (fr) * 1997-02-28 1998-09-04 Toyoda Automatic Loom Works Compresseur a deplacement variable et procede de fabrication d'un tel compresseur pour conditionneurs de vehicules
US5882179A (en) * 1995-11-24 1999-03-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor with bearing between the drive shaft and the swash-plate boss
US5931079A (en) * 1997-03-25 1999-08-03 Zexel Corporation Variable capacity swash plate compressor
EP1001169A2 (en) 1998-11-10 2000-05-17 Ford Motor Company Variable capacity swash plate type compressor
US6139282A (en) * 1997-02-28 2000-10-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity refrigerant compressor with an aluminum cam plate means
EP0907020A4 (en) * 1997-01-24 2001-03-28 Kk SWASH DISC BEARING FOR A COMPRESSOR WITH VARIABLE DISPLACEMENT
US6227811B1 (en) * 1998-10-11 2001-05-08 Visteon Global Technologies, Inc. Variable capacity swash plate type compressor
EP0949033A3 (en) * 1998-04-09 2002-03-13 Black & Decker Inc. Reciprocating saw with pivoted arm drive
US6397794B1 (en) 1997-09-15 2002-06-04 R. Sanderson Management, Inc. Piston engine assembly
US6460450B1 (en) 1999-08-05 2002-10-08 R. Sanderson Management, Inc. Piston engine balancing
JP3416738B2 (ja) 1999-12-16 2003-06-16 漢拏空調株式会社 可変容量型斜板式圧縮機
EP1148241A3 (en) * 2000-04-18 2004-03-03 Kabushiki Kaisha Toyota Jidoshokki Hinge mechanism for a variable displacement compressor
US20050005763A1 (en) * 1997-09-15 2005-01-13 R. Sanderson Management, A Texas Corporation Piston assembly
US6854377B2 (en) 2001-11-02 2005-02-15 R. Sanderson Management, Inc. Variable stroke balancing
US6913447B2 (en) 2002-01-22 2005-07-05 R. Sanderson Management, Inc. Metering pump with varying piston cylinders, and with independently adjustable piston strokes
US20050207907A1 (en) * 2004-03-18 2005-09-22 John Fox Piston waveform shaping
US7011469B2 (en) 2001-02-07 2006-03-14 R. Sanderson Management, Inc. Piston joint
US20060222513A1 (en) * 2005-03-04 2006-10-05 Masaki Ota Swash plate type variable displacement compressor
US7140343B2 (en) 2002-05-28 2006-11-28 R. Sanderson Management, Inc. Overload protection mechanism
US20060285981A1 (en) * 2005-06-21 2006-12-21 Visteon Global Technologies, Inc. Swash ring compressor with spherical bearing
US7325476B2 (en) 2004-05-26 2008-02-05 R. Sanderson Management, Inc. Variable stroke and clearance mechanism
US20080028926A1 (en) * 2006-08-01 2008-02-07 Visteon Global Technologies, Inc. Swash ring compressor
US7331271B2 (en) 2001-02-08 2008-02-19 R. Sanderson Management, Inc. Variable stroke/clearance mechanism
US20080052923A1 (en) * 2006-08-29 2008-03-06 Credo Technology Corporation, Robert Bosch Gmbh Drive mechanism for a reciprocating saw
US20100150744A1 (en) * 2007-03-29 2010-06-17 Ixetic Mac Gmbh Air conditioning compressor
US20100282071A1 (en) * 2007-11-21 2010-11-11 Doowon Tecnical College Variable displacement swash plate type compressor
US20100316510A1 (en) * 2008-02-21 2010-12-16 Ixetic Mac Gmbh Reciprocating piston machine
US20110041682A1 (en) * 2006-09-08 2011-02-24 Hiroyuki Makishima Variable capacity compressor

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DE19549566C2 (de) * 1994-04-15 2002-04-18 Toyoda Automatic Loom Works Kolbenverdichter mit variabler Verdrängung
DE19616961C2 (de) * 1996-04-27 2002-11-07 Daimler Chrysler Ag Hubkolbenmaschine mit Taumelscheibengetriebe
GB2358891B (en) * 1997-03-03 2001-12-05 Luk Fahrzeug Hydraulik A compressor for an air conditioning system in a motor vehicle
JPH10306773A (ja) * 1997-03-03 1998-11-17 Luk Fahrzeug Hydraulik Gmbh & Co Kg 特に車両の空気調和装置のための圧縮機
JP4280317B2 (ja) * 1997-03-03 2009-06-17 ルーク ファールツォイク−ヒドラウリク ゲーエムベーハー ウント コー． カーゲー 特に自動車の空調設備のための圧縮機
JPH1193833A (ja) * 1997-09-17 1999-04-06 Toyota Autom Loom Works Ltd 可変容量型斜板式圧縮機
US6249979B1 (en) * 1998-08-13 2001-06-26 Milwaukee Electric Tool Corporation Orbital reciprocating saw
US6210124B1 (en) 2000-01-27 2001-04-03 Ford Global Technologies, Inc. Variable swash plate compressor
US6354809B1 (en) 2000-01-27 2002-03-12 Ford Global Technologies, Inc. Variable swash plate compressor
US9765764B2 (en) 2014-04-07 2017-09-19 Hanon Systems Hinge mechanism for a variable displacement compressor
ES2937207B2 (es) * 2021-09-23 2023-07-31 Moran Emiliano Fernandez Bomba de pistones axiales

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
US5540559A (en) * 1993-04-08 1996-07-30 Ube Industries, Ltd. Variable capacity swash-plate type compressor
US5573379A (en) * 1994-04-21 1996-11-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity swash plate type compressor
US5638736A (en) * 1994-06-07 1997-06-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wave cam type compressor
EP0748936A1 (en) * 1995-06-05 1996-12-18 Calsonic Corporation Variable displacement swash plate type compressor
US5897298A (en) * 1995-06-05 1999-04-27 Calsonic Corporation Variable displacement swash plate type compressor with supporting plate for the piston rods
EP0759505A3 (en) * 1995-07-27 1997-03-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US5882179A (en) * 1995-11-24 1999-03-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor with bearing between the drive shaft and the swash-plate boss
EP0907020A4 (en) * 1997-01-24 2001-03-28 Kk SWASH DISC BEARING FOR A COMPRESSOR WITH VARIABLE DISPLACEMENT
FR2760257A1 (fr) * 1997-02-28 1998-09-04 Toyoda Automatic Loom Works Compresseur a deplacement variable et procede de fabrication d'un tel compresseur pour conditionneurs de vehicules
US6139282A (en) * 1997-02-28 2000-10-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity refrigerant compressor with an aluminum cam plate means
US5931079A (en) * 1997-03-25 1999-08-03 Zexel Corporation Variable capacity swash plate compressor
US7185578B2 (en) 1997-09-15 2007-03-06 R. Sanderson Management Piston assembly
US7040263B2 (en) 1997-09-15 2006-05-09 R. Sanderson Management, Inc. Piston engine assembly
US20050005763A1 (en) * 1997-09-15 2005-01-13 R. Sanderson Management, A Texas Corporation Piston assembly
US6397794B1 (en) 1997-09-15 2002-06-04 R. Sanderson Management, Inc. Piston engine assembly
US6446587B1 (en) 1997-09-15 2002-09-10 R. Sanderson Management, Inc. Piston engine assembly
US7007589B1 (en) 1997-09-15 2006-03-07 R. Sanderson Management, Inc. Piston assembly
US6925973B1 (en) 1997-09-15 2005-08-09 R. Sanderson Managment, Inc. Piston engine assembly
US6915765B1 (en) 1997-09-15 2005-07-12 R. Sanderson Management, Inc. Piston engine assembly
US20050039707A1 (en) * 1997-09-15 2005-02-24 R. Sanderson Management, Inc., A Texas Corporation Piston engine assembly
EP0949033A3 (en) * 1998-04-09 2002-03-13 Black & Decker Inc. Reciprocating saw with pivoted arm drive
US6227811B1 (en) * 1998-10-11 2001-05-08 Visteon Global Technologies, Inc. Variable capacity swash plate type compressor
EP1001169A2 (en) 1998-11-10 2000-05-17 Ford Motor Company Variable capacity swash plate type compressor
US6460450B1 (en) 1999-08-05 2002-10-08 R. Sanderson Management, Inc. Piston engine balancing
US6829978B2 (en) 1999-08-05 2004-12-14 R. Sanderson Management, Inc. Piston engine balancing
US20050076777A1 (en) * 1999-08-05 2005-04-14 R. Sanderson Management, Inc, A Texas Corporation Piston engine balancing
JP3416738B2 (ja) 1999-12-16 2003-06-16 漢拏空調株式会社 可変容量型斜板式圧縮機
EP1148241A3 (en) * 2000-04-18 2004-03-03 Kabushiki Kaisha Toyota Jidoshokki Hinge mechanism for a variable displacement compressor
US7011469B2 (en) 2001-02-07 2006-03-14 R. Sanderson Management, Inc. Piston joint
US7334548B2 (en) 2001-02-07 2008-02-26 R. Sanderson Management, Inc. Piston joint
US7331271B2 (en) 2001-02-08 2008-02-19 R. Sanderson Management, Inc. Variable stroke/clearance mechanism
US7162948B2 (en) 2001-11-02 2007-01-16 R. Sanderson Management, Inc. Variable stroke assembly balancing
US6854377B2 (en) 2001-11-02 2005-02-15 R. Sanderson Management, Inc. Variable stroke balancing
US6913447B2 (en) 2002-01-22 2005-07-05 R. Sanderson Management, Inc. Metering pump with varying piston cylinders, and with independently adjustable piston strokes
US7140343B2 (en) 2002-05-28 2006-11-28 R. Sanderson Management, Inc. Overload protection mechanism
US7438029B2 (en) 2004-03-18 2008-10-21 R. Sanderson Management, Inc. Piston waveform shaping
US20050207907A1 (en) * 2004-03-18 2005-09-22 John Fox Piston waveform shaping
US7325476B2 (en) 2004-05-26 2008-02-05 R. Sanderson Management, Inc. Variable stroke and clearance mechanism
US20060222513A1 (en) * 2005-03-04 2006-10-05 Masaki Ota Swash plate type variable displacement compressor
US20060285981A1 (en) * 2005-06-21 2006-12-21 Visteon Global Technologies, Inc. Swash ring compressor with spherical bearing
US20080028926A1 (en) * 2006-08-01 2008-02-07 Visteon Global Technologies, Inc. Swash ring compressor
US7444921B2 (en) 2006-08-01 2008-11-04 Visteon Global Technologies, Inc. Swash ring compressor
US20090060757A1 (en) * 2006-08-01 2009-03-05 Theodore Jr Michael Gregory Swash ring compressor
US7647859B2 (en) 2006-08-01 2010-01-19 Visteon Global Technologies, Inc. Swash ring compressor
US20080052923A1 (en) * 2006-08-29 2008-03-06 Credo Technology Corporation, Robert Bosch Gmbh Drive mechanism for a reciprocating saw
US7797841B2 (en) * 2006-08-29 2010-09-21 Robert Bosch Gmbh Drive mechanism for a reciprocating saw
US20110041682A1 (en) * 2006-09-08 2011-02-24 Hiroyuki Makishima Variable capacity compressor
US20100150744A1 (en) * 2007-03-29 2010-06-17 Ixetic Mac Gmbh Air conditioning compressor
US8353680B2 (en) * 2007-03-29 2013-01-15 Ixetic Mac Gmbh Air conditioning compressor
US20100282071A1 (en) * 2007-11-21 2010-11-11 Doowon Tecnical College Variable displacement swash plate type compressor
US8517695B2 (en) * 2007-11-21 2013-08-27 Doowon Technical College Variable displacement swash plate type compressor
US20100316510A1 (en) * 2008-02-21 2010-12-16 Ixetic Mac Gmbh Reciprocating piston machine
US8747077B2 (en) * 2008-02-21 2014-06-10 Ixetic Mac Gmbh Reciprocating piston machine

Also Published As

Publication number Publication date
JP2626292B2 (ja) 1997-07-02
DE4290950T1 (enrdf_load_stackoverflow) 1993-04-01
KR960001567B1 (ko) 1996-02-02
JPH04303184A (ja) 1992-10-27
DE4290950C2 (de) 1997-05-07
USRE35878E (en) 1998-08-25
KR920018351A (ko) 1992-10-21
WO1992017705A1 (en) 1992-10-15

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